Carburetor



March 3, 1953 E. RIVQCHE 2,630,304

CARBURETOR Filed Aug. 11, 1949 4 Sheets-Sheet 1 Patented Mar. 3, 1953 UNITED STATES PATENT OFFICE CARBURETOR Eugene Rivoche, Washington, D. 0.

Application August 11, 1949, Serial No. 109,787

Claims.

This invention pertains to a metering device and, more particularly, to carburetors for regulating and controlling the supply of the air-fuel mixture to internal combustion engines and the like.

It is an object of this invention to provide a carburetor provided with one or more adjustable jets adapted for use with the same ordifferent fuels, and adapted to be simultaneously or serially .used.

Another object of the invention is to provide the carburetor for an internal combustion engine wherein there can only be a full synchronization in the mixture of air and fuel, in desired and easily adjustable proportions of air and fuel.

Another object of the invention is to provide a carbureting or metering device for an internal combustion engine wherein the carburetor acts not only as a carburetor, but also may be utilized as a mixer of fuels of different character.

Another object of the invention is to provide a carburetor for an internal combustion engine which operates under pressure supplied by the usual fuel pump and not only by aspiration of the engine.

Another object of the invention is to provide a carburetor which does not utilize a float, thus there is no reservoir of liquid adjacent the engine which could be ignited accidentally.

Another object of the invention is to provide a carburetor wherein the adjustment thereof can be effected while the internal combustion engine with which it is associated is in operation.

Another object of the invention is to provide 'a carburetor which may be adjusted at any time permitting adjustments for differences in temperature, differences in pressure, or differences in grade of fuel, all such adjustments being possible while the engine is in operation.

Another object of the invention is to provide a carburetor for an internal combustion engine which permits an easy adjustment and quick control of fuel consumption, whereby the internal combustion engine associated therewith can be operated as economically and efiiciently as possible, and wherein the utmost performance can be attained, all such adjustments being possible while the engine is in operation.

Another object of the invention is to provide a carburetor which is positive of operation whereby it causes the engine with which it is associated to start immediately, whether the temperature is low or not, and regardless of the aspiration of the engine, and one wherein there :is no dependence upon fuel level, and wherein gradual,

there is always a proper mixture of air and fuel.

Another object of the invention is to provide an inexpensive, easily operated, adjusted and repaired carbureting device for an internal combustion engine which will operate in any position of such device. I

Another object of the invention is to provide a carbureting device for an internal combustion engine which is so constructed and arranged that overly large quantities of fuel cannot be supplied to the engine so there can be no flooding of the engine, nor can there be any vapor lock, and there is no danger that the unburned part of the fuel will mix with the lubricating oil or be dangerously expelled from the exhaust.

Another object of the invention is to provide a carburetor which is so constructed and arranged that it is self-cleaning, yet is easily regulated even While the engine is in operation.

Another object of the invention is to provide a carburetor for an internal combustion engine wherein a jet, or a plurality of jets, is provided which can be so adjusted as to provide, in effect, an infinite number of selected sized jets.

Another object of the invention is to provide a carburetor which is so constructed and arranged that a plurality of different fuels may be mixed in the carburetor for the supply to an internal combustion engine, the amount of such fuels being selectively variable.

Another object of the invention is to provide 'a carburetor wherein not only the supply of fuel can be varied during operation of the engine, but

' the richness and composition of the air fuel-mixl carburetor so constructed and arranged" that it is readily interchangeable with engines of dilfere'nt size within a reasonable range, of course, the only substantial essential being one of adjustment.

Another object of the invention is to provide a carburetor so constructed and arranged that even acceleration can be attained throughout the entire speed range. I

Another object of the invention is to provide a carburetor so constructed 'and arranged that the fuel inlet as well as the air inlet can be composed of unmatched parts, or unmatched parts may be used in both inlets to obtain the desired operational results.

Another object of the invention is to provide a carburetor so constructed and "arranged that fuel inlets are utilized which may come into operation at different degrees of throttle opening to act as an acceleration pump or-to actto help maintain Figure 1 is an elevation, partly in section, of

one form of carburetor embodying the invention Figure 2 is an enlarged, fragmentary elevation of the inner end of the injection ornozzle members of the carburetor illustrated in Figure 1;

Figure 3 is an end elevation of the orifice illustrated Figure 2- showing the. relative position ofithe ports for nozzle members. illustrated in Fi ur Figures. is a sectional. elevation, through. the nozzle; members illustrated in Figures 1 to 3, in-

clusive, the same being taken substantially in the plane as indicated by the line. 4-4 of Fi ure. 1;

Figure 5 is a fragmentary, sectional elevation of a modified form of. carburetor. embodying the invention;

Figuresfi and 7 arev fragmentary, sectional. elevations ofmodified forms of injection members for carburetors embodying, the. invention, Figure '7 showing associated injectionmembers having a modified form of air flow control for. the fuel supply through said injection members;

Figure 8. is: a fragmentary, sectional elevation of; another modified form of air fiow control ofthe fuel supply of a carburetor. embodying the invention;;

Figure-9 is a. fragmentary, sectional elevation of. a vacuum control device for controlling the fuel cut-off of injection members ina carburetor embodying the invention;

Figure 10 is a fragmentary, sectional elevation of anacceleration vacuum control device, for a carburetor embodying the invention;

Figure 11 is, a fragmentary, sectional elevation through a modified form of injection members for carburetors embodying the. invention, illustrating control meansv for the air supply during idling position of the carburetor;

Figure 11a; is a perspective elevation of anagitating devicefor use in place of a part. of. the device shown in Figure 11;

Figure 12. is, a. fragmentary, sectional elevation of av form. of. control device for, controlling the fuel supply-,7 as: from the supply pump to the. carburetor injector of a carburetor embodying the invention, the same showing the valves in open position, that is, in a position where acceleration is taking place;

Figure 13 is a fragmentary, sectional elevation corresponding to Figure 12 but showing the inlet valve in closed position, that is, the engine is stopped and the. fuel flow is cut off.

Figure 14 isa sectional elevation corresponding to Figure 12 whereinthe inlet valve is open but the valve controlling acceleration is closed, that is, the device is in idling position;

Figure 15 is a sectional elevation through a still different form of carburetor embodying the invention, wherein the fuel and air supply control means ar operative about a common axis, the section being taken substantially in the plane as indicated by the line l5-I5 of'Figure 16;

Figure 16 is a sectional plan view taken substantially in the plane as indicated by the line l6--I6 of Figure 15;

Figure 17 is a fragmentary, side elevation of the carburetor illustrated in Figures 15 and 16, particularly showing the air inlet control;

Figures 18 and 19 are perspective elevations of forms of cylindrical air valves for carburetors embodying, the inventions; showing different forms of air openings to obtain disproportionate air inlets upon proportionate operation of said valves; and,

Figures 20 and 21 are modified forms of disk valves adapted to be substituted for the conventional disk. valve used in many conventional carburetors for controlling the air inlet in the same manner as the valves shown in Figures 18 and 19 control the air inlet in the herein disclosed carburetor.

Beferringfirst of all,more particularly, tothe form of carburetor illustrated in Figure 1, said carburetor includes a stationary casing 30 having a .flang e 32 adapted to be connected to, the inlet manifold of an internal combustion engine.

Casing 30 is provided with the mixture outlet passage 34 adapted to conduct the mixed air and fuel from mixing chamber 35 to the inlet manifold, and mixing chamber 36 also communicates through intake passage 38 to the atmosphere as through a suitable air filter (not shown). Passages 34 and 38 are preferably substantially cylindrical, the axes thereof being coextensive, i. e., if a section is taken through either passage in a plane normal to the axis, it is circular. Casing 30 is provided with the cylindrical bore 40 in which the cylindrical air control valve 42 is rotatably mounted, the axis of said bore and air valve being normal to the common axis of pegsages 34 and 38. Inasmuch as valve 42 is cylindrical, the mixing chamber 36 is directly within said valve. The end of valve 42 is provided with the inlet orifice or port 44 adapted to register with the air intake passage 38, and said valve 42 is also provided with the outlet orifice or port 46 adapted to similarly register with the mixture outlet passage 34.

The ends of the cylindrical valve 42 are closed by the end closure webs 48 and 50 of the outer injection or nozzle members 52 and 54, the axes of which are disposed on the axis of the valve 42, the ends of said outer injection members, which project within the mixing chamber 3'3, terminating in spaced relation to each other, being substantially frustoconical.

Webs 48 and 50 are fastened to thecylindrical valve 42 in such a manner that they can be changed in their relative positions with respect to the cylindrical valve so that they can be disposed in different positions, as for example positions disposed 90 apart for the purpose to be later described. In order to rotate the cylindrical valve 42 and to rotate the outer nozzle members 52 and 54 to vary the positions of the (air) inlet and (mixture) outlet ports 44 and 46 with respect to passages 38 and 34, respectively, a suitable lever 55 is fixedly secured to one of the outer projections 58 or 60 (shown 58) of the outer nozzle members 52 or 54.

The outer nozzle members are threaded as at 62 and closure caps 68 and 10 are threaded to the respective outer nozzle members pressing spring 12 between the adjacent cap and the spring seat or shoulder I4 on the inner stationary nozzle or injection member 16 (and 18). Nozzle member (and 18) is connected to a suitable source of fuel supply through a supply pump (not shown), the inner nozzle members being provided with a fuel passage 98 adapted to be connected through port 02 to the outlet side of said supply pump. Adjustment means as described particularly in applicants application Serial No. 18,439, filed April 1, 1948, for Carburetor, may be provided for adjusting port 82 as from the dash, or for adjusting inner nozzle member I6 (18) and consequently, the injection ports to be later described. Such adjustment may be made as for varying the operating mixtures where the nozzles inject the same or different fluids. Also, where nozzles are to be used selectively alone, or together.

The outer end 84 of the inner nozzle member is closed by means of the cap 86 provided with a suitable gland or stufling box 00 through which the valve stem 90 passes. The inner end 92 of the inner nozzle member I6 (18) is frustoconical, being adapted to be of complementary shape to the frustoconical inside portion of the outer nozzle member 52 (54) disposed within the mixing chamber. The inner end 92 of the inner injection members is provided with port 94 which communicates with the frustoconical end 96 of passage 98, passage 98 communicating with port 82. Port 94 is adapted to be controlled by the needle valve I00 secured to stem 90, the position of said valve I00 being controlled by said stem. Stem 90 may be adjusted at cap 06 or remotely adjusted as through a flexible shaft to the dash.

The inner end 92 of the inner injection member is also provided with ports I02, shown as four in number, disposed substantially 90 apart (Figure 4), said ports I02 communicating with passage 98. Ports I02 and 94, as shown, are of substantially circular section. The selected one of the ports I 02 is adapted to communicate with the elongated port I04, which, as shown, is disposed in a plane which is at an angle (not 90) to the axis of the injector members, or in effect, said port is contoured to control the opening and closing of port I02 in the desired manner to obtain the desired gasoline supply from passage 98 to the mixing chamber 36. The operative port I02 which is controlled by port I04 is determined by the positioning of web 4.8 (50) in its selected position on valve 42.

Port 94 is controlled by one of the contoured ports I06, which ports I06 are shown as four in number (Figure 3), the operative one of said ports with respect to port 94 being determined by the selected position of web 48 (50) on valve 42. It will thus be appreciated that the position of webs 48 and 50 with respect to the valve 42 determines which port I06 controls port 94, and, also, which port I02 is controlled by port I04.

In order to control the air inlet to the mixing chamber 36, valve 42 is rotated, whereby port 44 controls the passage of air through passage 38 to said mixing chamber. The same rotation also controls the flow of the mixture from the mixing such that it opens the designed disproportionate amount for a proportionate opening of the air tween the air and supplied fuel as the throttle is moved. With this construction having once been selected, the selected air-fuel ratio is maintained at any R. P. M. of the engine.

Port I04 is positioned so that it starts to open (operative) port I 02 when air valve 42 is in a predetermined position, and port I02 is in maximum open position at the time that the air valve is in its maximum open position, at which time port 94 (I06) is in its maximum open position. Ports I02, I04, 94 and I06 are so relatively positioned with respect to the air valve that at the time acceleration is initiated an enriched mixture is supplied to the manifold independent of the velocity of the air, because the ports are so positioned and shaped that an additional amount of fuel is supplied to the mixing chamber through ports 94 and I06 at the time acceleration is initiated. This additional supply of fuel normally causes an enriched mixture to be supplied to the manifold, which causes acceleration, but as the speed of the engine increases, and inasmuch as the gasoline supply through the port 94 is not increased with the increase of speed of the air velocity due to the increase in speed of the engine, the air-fuel ratio tends to return to the selected air-fuel ratio. However, port I02 having been opened by port I04 during the opening of the air valve during accelerating operation, said port I02 (I04) supplies an additional amount of fuel which maintains the enriched air-fuel ratio during the entire accelerating range.

Referring now to the modification illustrated in Figure 5, the carburetor comprises the easing I08 (similar to casing 30), said casing having the securing flange IIO adapted to be secured to a manifold of an internal combustion engine,- and is provided with the cylindrical bore II2 (similar to bore 40) for accommodating the cylindrical air control valve II4. Valve H4 is provided with the air inlet port I I6 and the mixture outlet port I I8, said ports communicating, respectively, with the air inlet passage I20 (similar to passage 38) adapted to be connected through a suitable filter (not shown) to the atmosphere, and to the mixture passage I22 (similar to passage 34). As before, the axes of passages I22 and I20 coincide and are normal to the axis of valve I I4.

The disposition of ports I I6 and H8 determine the communication between atmosphere and mixing chamber I24, and between said mixing chamber and the manifold. Only one injection member is illustrated, but it is understood that either only one is adapted to be used, or a plurality may be used such as illustrated in Figure 1. Where only one is used, the radial flange I26 of the cylindrical valve is adapted to be closed by a plain cover plate. Where a plurality are used the construction to be described is provided in duplicate as shown in Figure 1.

The injection assembly, indicated generally as at I28, is disposed on the axis of rotation of the cylindrical air-valve II4, as certain of the injection members rotate therewith. The outer injection member I30 is provided with the radial closure flange or Web I32 adapted to be secured to the radial flange I34 of the cylindrical valve and, as before, is adapted to be positioned in four different positions, spaced apart (or other selected spacing may be used, the number of which spacings determining the number of ports of the injection assembly which communicate with the mixing chamber). The outer injection member is provided with the inwardly directed i'rusto-conical member I36 having a similar inner bearing surface adapted to have bearing cooperation with a complementary frusto-conical surface I38 of the inner injection member I40. The inner injection member I40 is shouldered as at I42, forming a spring seat for the retaining spring I44, which is interposed between said shoulder and the closure cap I46 threadedly secured to the outwardly projecting member I48 of the outer injection member I30.

The inner injection member I49 is threaded internally as at I50, providing securing means for the threaded projection of base I52 of the bellows housing I54. The upper bellows housing member I56 is threadedly secured as at I58 to base I52. The flexible, collapsible bellows I60, of substantially toroidal form, is disposed within bellows housing I54 displacing a certain volume in said housing, one side of said bellows being secured to the base I52. The inside of said bellows communicates with mixing chamber I24 through passage I62, which passes through a portion of the base member I52 and the inner injection member I40.

Base member I52 and inner injection member I40 are also provided with an axially disposed passage I64 terminating in a valve seat I66 for the needle valve I68. The needle valve is adapted to control the passage I (similar to passage 94) communicating with the port I12 (similar to port I06) in outer injection member I36 shaped similarly for the same purpose as port I36. Passage I10 communicates with passage I14 which in turn communicates with a valve passage I16 in which a spring pressed valve I18 is urged toward closed position by means of the spring I80, said valve seating on the seat I82 which controls the passage I84 communicating with the bellows housing externally of the bellows. Valve I18 seats toward passage I84.

Top bellows housing member I56 is provided with the extension I86 threaded as at I88 for the reception of the securing cap I90. Cap I90 serves as a seat for one end of spring I92 seated at the other end on the shoulder I94 of the valve stem guide member I96, said member being provided with the frusto-conical surface complementary to and fitting within the frusto-conical surface I91 provided on the extension member I86.

Housing I54 is provided with the boss I93 which in turn is provided with the valve housing 200 within which is disposed the spring pressed valve 202 seating on seat 204, being urged toward closed position by means of the spring 206. Valve 202 controls passage 208 communicating with a source of fuel supply, and the inside of said housing 200 communicates through passage 2I0 with the inside of the bellows housing I54 externally of the bellows I60. Valve stem 2I2 of the valve IE8 is disposed on the axis of the nozzle and extends outwardly of the stem closure member 96, being provided with means, such as a manual adjusting screw 2I4 whereby the position of the nozzle valve may be adjusted to control the opening of passage I10.

In the operation of this device a suitable lever, not shown, similar to lever 56 (Figure 1) is provided for rotating the cylindrical valve H4 and the outer nozzle member whereby port I12 is controlled and functions similarly to port Hi6 (Figure 1) already described. Fuel will be supplied from the source as by the fuel pump (not shown) and will flow past valve 202 and will fill the bellows housing chamber externally of the bellows I60, and the bellows will be collapsed by the pump pressure plus the vacuum in the mixing chamber acting on the inside of the bellows through passage I62, but the pump pressure plus the suction (vacuum) in the mixing chamber will not be sufficient at this time to open valve I18. When the vacuum decreases within the mixing cham her, the vacuum acting within the bellows I60 through passage I62 will drop, permitting the bellows to expand, whereupon the pressure will increase on valve I18 sufficiently to overcome the spring I80, whereupon a quantity (shot) of fuel will be supplied through passage I14, passage I10 and through port I12 to the mixing chamber, thereby increasing the amount of fuel supplied thereto to be mixed within said chamber and supplied through the port M8 to the manifold through passage I22. The expansion of the bellows will be effective to cause this shot, as fuel will not back up into the supply line when bellows I00 expands as valve 292 will close preventing this backing up.

When the vacuum is again raised within the mixing chamber I24, it will act on the inside of the bellows, through passage I62, causing said bellows to move toward collapsed position, whereupon mcre fuel is permitted to be supplied past valve 202 to the inside of bellows housing I54 and fuel will be supplied through passage I30 and port I12, in which case valve I18 will be closed. Thus with this device enrichment occurs in somewhat the same manner as where a separate pump is actuated for acceleration purposes but in this case the enrichment is dependent upon changes in pressures in the engine manifold as a result of changes in the throttle position.

Referring to the nozzle or injection member illustrated in Figure 6, said injection member comprises an outer casing or injection member 2I6 which is preferably disposed on the axis of the end closure for the air valve such as illustrated in Figure l, but is non-rotatable. The injection member 2 I6 is provided with the passage 2I8 communicating with the supply pump connected to a source of fuel supply, the passage terminating in a conical valve seat 226 disposed adjacent the port 222. The valve seat is adapted to be controlled by the needle valve 224 which, in turn, is controlled through stem 226, said stein being controlled manually or through suitable pressure devices such as will be, more particularly described with respect to Figures 8, 9, 10 and 12 to 14. Passage 222 communicates with chamber 228 disposed in the injection member 2I6 and closed by the closure 230. Closure 230 is provided with the valve seat 232 adapted to be controlled by the valve member 234 controlling the passage of fuel into the mixing chamber.

Valve member 234 is substantially frusto-conical, having a portion disposed outwardly of the chamber 228 and within the mixing chamber where it can be acted upon by the passage of air, and once the valve member is open, by the passage of fluid (air-fuel mixture) passing therethrough. The valve member is so disposed that it is adjacent the mixture outlet passage as 34 in Figure 1, the axis of the valve member extending in the same direction as the axes of passages 34 and 38. Valve 234 within the chamber 228 is contoured as at 236 whereby the port 232 is controlled in the same manner as al- .through the carburetor. the injection member 268 provided with the pasready described with respect to port I66, Figure 1. Valve 234 is provided with the stem 238 passing through suitable packing 246 so that there can be no leakage around the stem, and extends upwardly, a spring 242 being interposed between injection member 2 l6 and the spring cap 244 secured as at 246 to the stem, urging the valve member toward closed position.

In the operation of this form of device, assuming valve member 234 to be closed, the velocity of the air passing through the carburetor will act on valve member 234, opening said valve member against spring 242, thereby permitting fuel to be supplied past the needle valve 224 and past valve 234 into the mixing chamber, The opening of the valve member will also be aided by the fuel pump pressure. The contour of the valve 234 determines the disproportionate opening of the fuel port as compared to the air flow as was described with respect to Figure 1.

In Figure 7, a valve control is illustrated wherein a plurality of fuel nozzles 248 and 256 are controlled by a single valve 252. As before, these nozzles are disposed on a common axis (coinciding with the axis of the air valve) and project within the combustion chamber but are non-rotatable with respect to the air valve, the aXis of the control valve for said nozzles preferably being in the direction of air flow through the carburetor. Each of said nozzle members 248 and 256 comprises a nozzle member 254 provided with a passage 256 communicating with a suitable pump of a source of fuel supply. Each passage is provided with the valve seat 258v adapted to be controlled by the needle valve 266.

Said needle valve 266 is provided with a contoured portion which controls the disproportionate flow of fuel past seat 258. Said needle valve is adapted to be controlled manually, or through suitable operating mechanism such as to be later described with respect to Figures 8, 9, 10 and 12 to 14. Passage 256 communicates with discharge passage 262 through which fuel is supplied to the mixing chamber of the carburetor such as illustrated in Figure 1. Passage 262 is adapted to be controlled by the valve 252 which may be conical in shape (or pear shaped), being urged toward closed position by means of the leaf spring 266 secured at its ends as at 266 to said nozzle members.

In this form of device it is the flow of air and the air fuel mixture aided by the supply pump pressure which controls the opening of valve 252 and, consequently the supply of fuel to the mixing chamber. Valve 252 can be contoured similar to valve 234 (236) in Figure 6, in which .of the carburetor, and is adapted to be controlled by the passage of air or air and fuel mixture The device comprises at 215 to the fuel pump connected to the source of fuel supply.

A spring seat 216 is threaded into the injection member 268 within passage 216 and is suitably apertured as at 218 to permit the passage of fuel therethrough. Passage 216 is provided with the valve seat 286 communicating with the inlet passage 282, which in turn communicates with the mixing chamber or one of the passages (as 34 or 38, Figure 1) through the carburetor. Valve seat 286 is normally abutted by the valve 284 to close the inlet passage 282, spring 286 being interposed between the valve and the spring seat 216 urging said valve toward closed position. Valve 284 is provided with the fluted or otherwise suitably shaped stem 288 extending through passage 282 to a point within the carburetor, and the injection member 268 is provided with the bracket 296 to which the actuating member 292 is pivoted as as 294. Actuating member 294 is provided with the contoured cam 296 disposed in engagement with the end of stem 268. This device is preferably disposed so that, in inoperative condition, with valve 284 closed the operating member 292 will extend toward the air flow, 1. e., the axis of injection member 268 will be normal to the axes of passages such as 34, and 38 of Figure 1.

In the operation of this device, assuming the air flow to be downwardly as viewed in Figure 8, when the air flow reaches a predetermined amount, operating member 292 will be moved in a counterclockwise direction about pivot 294, causing the cam 296 to depress the stem 288 in accordance with the contour of the cam, opening the valve 286, whereby a disproportionate amount of fuel can be supplied within the carburetor in a manner similar to that supplied through the ports I66 (or I64) as shown and described with respect to Figure 1.

In the construction illustrated in Figures 9 and 10, the fuel supply line 296 is adapted to be connected as to an injector having port supplying iuel within the mixing chamber of a carburetor as through port 64 in Figure 1. However, in Figures 9 and 10 the needle valve, which may be a plain needle valve or a contoured one as shown in Figure 7, may be placed remotely .from port 94. Supply line 296 is provided with the valve seat 268 normally abutted by the needle valve 366.

In the modification illustrated in Figure 9 valve stem 362, of the needle valve 366, passes through a suitable stuffing box or gland 364 as in an elbow in line 296, and is secured to the movable seat member 366 disposed in the housing 368. A spring 3I6 is interposed between the seat memher 368 and a seat 3l2 on the cover 314 of the housing 368, said spring with the bellows 3l6,

urging the valve 366 toward closed position. Flexible, collapsible bellows 3I6 is secured at one end to the seat member 366 and at the other end to seat member 3I2, thus being a closed member, the bellows acting in the same direction as the spring, that is, toward valve closing position. The inside of the bellows is connected through pipe 3 I 8 to the carburetor, as for example, to passage 34 in Figure 1. Therefore, in the case of Figure 9 the vacuum Within the carburetor will tend to collapse bellows 316 and, consequently, tend to open valve 366. Thus a fluctuation in vacuum causes movement of the valve 366 to control the passage of fuel in accordance with the movement of the contour of the valve 366.

In the case of the construction illustrated in Figure 10 the valve stem 362 passes through a stuffing box or gland 326, as in an elbow of the supply line 296, and is secured to bellows end plate 322 as at 324. Stuffing box 326 is in end plate 326 to which one end of the bellows 328 is secured, the opposite end of said bellows being secured to plate 322. Flexible, collapsible bellows 32B is of substantially toroidal shape, and of course, the bellows and end plates may be disposed in a housing such as 308 (Figure 9). The bellows acts in a direction to separate plates 322 and 326, and spring 330 may also be interposed between said plates acting in the same direction, that is, to urge valve 300 toward open position. Pipe 332 is connected at one end to the inside of the belows 328 and at the other end to the carburetor suction, as to passage 34 (Figure 1). In Figure the vacuum in the carburetor controls valve 300, which may be contoured, or plain, as desired, a rise in vacuum tending to move the valve toward closed position, and a fall in vacuum operating the valve in the reverse direction. Such a form of device might be useful for injecting special fuel components into the engine when the vacuum in the carburetor is low, or as a form of acceleration pump when the vacuum is decreased by a sudden opening of the throttle.

In the device illustrated in Figure 11 there is illustrated mechanism whereby injection means is provided as for a carburetor such as illustrated in Figure 1, and wherein a rotary air valve is used such as air valve 42 in casing 34 (Figure 1). In this case an injector (at one or both sides of the air valve) comprises the outer injection member 334 (similar to injection member 52 (Figure 1), provided with the closure web 336 for closing an end of the air valve, such as valve 42 Figure 1. Said outer injection member is rotatable with the air valve, as described in Figure 1, and is provided with contoured ports 338 and 346, similar to ports I04 and I06. The inner, non-rotatable, injection member 342 is provided with the conical end 344 fitting within the inner conical end of the outer injection member, and is provided with ports 346 and 348, similar to ports I02 and 94, respectively, of Figure 1.

The inner injection member is suitably retained in assembly with the outer injection member, and is provided with the passage 350 for supplying fuel to ports 346 and 348, said passage 350 being closed by cap 352 to which the fuel supply pipe 354 is connected. The fuel supply line is adapted to supply fuel through a suitable pump from the source of supply to the inner injection member. Fuel supply pipe 354 may be controlled as in the case of fuel supply line 296 (Figure 9) by the needle valve and control means therefor. As before pointed out, the control device illus-- trated in Figure 9 is a control using the engine vacuum, wherein the fuel valve 300 is closed when the engine is inoperative, at which time the fuel supply is cut off from the nozzle. The control device illustrated in Figure 10, while vacuum controlled, is adapted to be operative during acceleration so that, if desired, in the device illustrated in Figure 11, both of the control devices illustrated in Figures 9 and 10 may be used, but where only one is used, that shown in Figure 9 is the one which is used.

An air supply line 356 is disposed axially of the injection assembly, passes through cap 352 through a fluid tight connection, and is secured to its inner end as at 358 to the end of the inner nozzle member 344. A baffle 360 is provided whereby the air supplied through pipe 356 is directed toward port 340. Bafile 360 may be eliminated, and some agitating means may be used in place thereof to facilitate mixing the air and fuel. By way of example, this agitating device may be the propeller 36I pivoted at 363 to shaft 365 which is adapted to be secured to member 344 so that it rotates in the mixing chamber. Other such devices may be used as helices, turbines, paddles, etc. Pipe 356 is provided with the valve seat 382 controlled by the needle valve 364, which is manually adjustable, as is indicated more or less diagrammatically as at 366, but thereafter is controlled by vacuum control mechanism, indicated generally as at 368, which is similar to that shown in Figure 9. This mechanism is vacuum controlled through pipe 310 similar to pipe 3I8 in Figure 9.

It will thus be seen that in the idling position, the air valve, such as air valve 42 (Figure 1), will be closed but valve 364 will be open, whereby idling air will be supplied within the mixing chamber. In this construction, in idling the air valve port controlling the inlet passage 38 (Fig ure 1), is closed, and either the valve controlling the passage 34 is eliminated or it is cracked open. As the cylindrical air valve is opened to permit air to be supplied through passage 38 in Figure 1, the vacuum control mechanism operates the control 368 to tend to close the needle valve 364, rendering the air supply through pipe 356 inoperative.

With the device illustrated in Figure 11 when the engine is inoperative, both the air supply and the fuel supply are cut off from the injector. With the conventional carburetor there is provided an air supply opening which is constantly open. Therefore, with the use of the conventional carburetor it is practically impossible to use vacuum controlled fuel cut-off devices which are operative as the engine is being started, as the starter motor does not reciprocate the pistons with sufficient speed to draw the necessary vacuum. Thus there is a tendency for the cut-off valve to remain closed which makes for difficult starting. With applicants device, just prior to starting by the starter motor, the idling air valve 364 is closed, as is the valve which controls the fuel supply through line 354. Inasmuch as the idling air valve 364, as well as the air control valve 42 (Figure 1) is closed, a vacuum is immediately established, even by the slow starting operation of the starter motor, which causes opening of the air supply valve 364 as well as the fuel supply valve to line 354, thus facilitating the starting operation of the engine. Thus, by the use of the control mechanism 368 in this manner, it is possible to use a vacuum control cut-off device as illustrated in Figure 9 to control the fuel line 354.

In Figures 12 to 14, inclusive, there is illustrated another type of control device for controlling fuel supply from the supply pump to the carburetor injector. This control device utilizes the vacuum as well as fuel supply pressure (supply pump pressure) to aid the opening of the valve controlling the supply line. This device comprises a body 312 closed at its ends as at 314 and 316, said body being provided with the chamher 318 having a valve seat 380 therein adapted to be closed by the valve 382. Valve 382 is secured to one closed end of bellows 384, the other end being closed by means of closure 316.

Vacuum line 386 communicates with the inside of bellows 384 and with manifold vacuum, as for example through passage 34 in Figure 1. Valve 382 is provided with the valve stem 388 extending through passage 390 and is provided with the valve 392 disposed in chamber 394. A fuel inlet supply line 396 communicates with 13 chamber 313 and with a suitable fuel pressure pump connected to a source of supply. Passage 396 communicates with the fuel line 398, which is connected to the mixing chamber of the carburetor, as through injector members such as illustrated in Figure 1.

Chamber 394 is connected through fuel supply line 483 with the carburetor in order to give an added shot of fuel as is desirable in accelerating, as through a connection to the passage 34 in Figure 1. This additional fuel supply is maintained during the whole period of acceleration, thus creating a special power circuit. Valve 392 permits connection between fuel inlet 396 and line 493 when said valve is open, and when closed on seat 462 out 01f connection between inlet 396 and line 460.

In this form of the device when the engine is in idling condition, valve 392 is closed on valve seat 462 and valve 382 is open (Figure 14) being maintained in open position both by the vacuum within the bellows 334, and by the fuel supply pressure of the fuel being supplied through line 396. When the engine is in inoperative condition, valve 332 is closed on its seat 386 (Figure 13). When the engine is started and is in its idling or normal speed position, vacuum acting within the bellows 384 will open valve 382 to a position where valve 392 is closed on its seat 492 (Figure 14). When acceleration takes place, there will be a drop in vacuum within bellows 384 so the valve 382 will move toward closed position, but will not completely close (Figure 12) However, the movement will be sufficient to open valve 392 permitting the shot of fuel desired for acceleration through the line 439, it being understood that fuel is also being supplied through line 398 to the carburetor.

Referring now to the form of device illustrated in Figures 15 to 17, inclusive, the carburetor as illustrated is arranged so that the air valve and the fuel supply valves are disposed on a common axis. This device comprises a base 464 adapted to be secured to the intake manifold of an engine. Base 464 is provided with the passage 496 therethrough for supplying the mixture to the manifold, and is provided with the radial flange 433 to which the fixed outer cylindrical shutter member M6 is secured as at 4l2. Shutter member 453 is provided with the spaced air openings 4E4 through which air passes as through filters (not shown). Inner movable cylindrical shutter member 416 is rotatably mounted on bearing surface 418 on flange 468, and said inner shutter member is provided with the air openings 429. Shutter member 416 is secured as at 422 to radial shutter member 424 provided with fixed openings 426 therethrough whereby, in effect, said member 424 is a spider.

Member 424 adjacent the vertical axis of shutters 4H] and 416 is provided with the downwardly extending conical wall 423 provided with contoured port 43%) therein similar to port I66 (Figure 1). Movable shutter M6 is secured as at 432 to the radial closure member 434 which is provided with the centrally disposed, downwardly extending conical nozzle member 436 provided with contoured openings 438 therein. It will thus be seen that members 424 and 434 rotate with shutter 416. Shutter 4H1 adjacent the top thereof is provided with a closure 446 secured thereto as at 442, and said cover, adjacent the center thereof, is provided with means for rotating the shutter 416, as by the throttle, which means may take the form of any convenient means, such as a gear 444 adapted to be rotated by said throttle. It is obvious that radial shutters disposed at the top of the cylindrical housing (Figs. 15 and. 17) of the carburetor could be substituted for the cylindrical shutter members M0 and 416.

Upper, inner injection member 446 extends through said cover plate 440 and is provided with the frusto-conical end 448 matching the upper cone surface of member 436, being maintained in fluid tight relation therewith by means of the spring 450 interposed between said cover plate 440 and the spring seat 452 on injection member 446. A fuel passage 454 is provided in injection member 446 and communicates with passages 456 controlled by ports 438. Lower, inner injection member 458 extends through injection member 446 and has a nozzle end 460 having a conical surface matching the inner conical surface of nozzle member 428. Injection member 458 is maintained in fluid tight relation to nozzle member 428 by means of spring 462 interposed between end member 458 and nozzle member 436.

Nozzle member 458 is provided with the fuel passage 464 communicating with passage 466, which is controlled by port 430. Port 430 is preferably also contoured in the same manner and for the same purpose as port H36 in Figure 1. In operation of this form of the device, it will be seen that the air openings M4 and 426 are controlled by rotation of shutter member 416 which at the same time controls the openings of ports 438 and 430, thus causing a functioning similar to that described with respect to the relation of ports [06 and I04 and the air ports in Figure 1.

In the form of carburetor illustrated in Figure l, for example, the cylindrical air valve 42 is provided with ports 44 and 46. These ports control flow from passage 38 into the mixing chamber 36, and from the mixing chamber into intake manifold through passage 34. It is convenient in manufacture for passages 38 and 34 to be circular in section. Ports 44 and 46, which control passages 38 and 34 by their position with respect thereto, may be of the selected shape so that a proportional movement of the cylindrical valve gives a disproportionate effective opening.

Examples of such ports are illustrated in Figures 18 and 19 wherein the cylindrical valves 468 and 416 are provided with such ports 412 and 414, respectively. The configurations of the ports are chosen to give the desired disproportionate opening.

In carburetors such as illustrated in the patent to Moorehouse No. 920,979, operation of the throttle causes a circular air inlet to be controlled by a circular closure which is rotated around a center spaced from the center of the air inlet. Thus a proportional movement of the throttle causes a proportional opening or closing of the air inlet. In order to cause a disproportionate opening or closing of the air inlet, devices such as illustrated in Figures 20 and 21 may be substituted for the circular closure of Moorehouse, which controls the circular air inlet. In Figure 20 there is shown a circular disk 416 utilized to completely close the air inlet. This is associated with a contoured disk 418 so shaped that as it moves over the air inlet a disproportionate amount of inlet opening is obtained for a proportionate movement of the throttle. Each of the disks 416 and 418 are adapted to be pivoted through suitable connected arms 480 to the throttle control.

A modified form of closure structure is illustrated in Figure 21. In this figure the outer closures 482 and 484 are provided with different contoured openings and the inner disk 486 is adapted to conform to the shape O e i inlet for closing said inlet. Said disks may be pivoted through arms 488 to the accelerator control means, and the accelerator may be selectively connected as at 490 and 492. In this form of air inlet control the center closure 48,6 is selectively used with either of the closures 482 or 484. And in each of the structures shown in Figures 20 and 21 the contours of the contoured disks is chosen in the same manner as the openings in the construction shown in Figures 18 and 19.

It is to be understood that this application is not to be limited by the exact embodiments of the device shown, which are merely by way of illustration and not limitation as various and other forms of the device will, of course, be apparent to those skilled in the art without departing from the spirit of the invention or the scope of the claims.

For example, although only two injection members have been shown and described in the embodiments illustrated, it is obvious that any desired number of such injection members could be similarly incorporated.

I claim:

1. In fuel metering mechanism for an internal combustion engine, the combination of a casing having an outlet adapted to be connected to the fuel mixture inlet of an internal combustion engine, said casing having an air inlet, the casing having a cylindrical bore, a cylindrical valve member rotatably mounted in said bore and provided with ports for controlling flow through said casing outlet and inlet, said rotary valve member and casing forming a mixing chamber, closures for the ends of said casing, one of said closures being rotatable and connected to said valve member, an injection device disposed on the axis of said valve member and extending into the mixing chamber, said injection device comprising an outer injection member fixed to said rotatable closure and having its axis disposed on the axis of said valve member, the nozzle end of said injection member being disposed in said mixing chamber, a second injection member mounted in said outer injection member and having a nozzle end extending into the nozzle end of said outer injection member, said outer injection member being non-rotatable with respect to said cylindrical valve member, said nozzle ends having iuel ports for controlling the passage of fuel to said mixing chamber, said outer injection member having a plurality of similar contoured ports spaced apart equidistantly and of varying shape and disposed in a plane normal to the axis of said valve member, said outer injection member being a single port in a plane at an angle to the axis of said valve member, the entrance of the single port being disposed adjacent the end one of the contoured ports, said inner injection member having a single port of substantially circular section adapted to be controlled by the selected one of said contoured ports whereby a disproportionate opening of said last named single port is eifected by a proportionate rotation of said cylindrical valve member and said outer injection member, said inner injection member having a plurality of equally spaced ports of substantially circular section in a plane normal to the axis of said circuls-r valve member, the selection of said last named ports being con r ll d. by a d fir t n me single port, rotation of the outer injection member rotating the valve member to vary the casing inlet and outlet and also rotate the ports of the outer injection member with respect to the ports of the inner injection member to vary the supply of fuel to said mixing chamber, and throttle means for simultaneously rotating the outer in jection member and said valve member, rotation of the outer injection member and said valve member serving to regulate the fuel ports with respect to the casing inlet and outlet to maintain a selected air-fuel ratio during the entire operation of the throttle means.

2. In fuel metering mechanism for an internal combustion engine, the combination of a casing having an outlet adapted to be connected to the fuel mixture inlet of an internal combustion engine, said casing having an air inlet, said outlet and air inlet comprising coaxial passages of substantially circular section, the casing having a cylindrical bore, the axis of which is substantially normal to the axis of said passages, a cylindrical valve member rotatably mounted in said bore and provided with ports for controlling flow through said casing outlet and inlet, said ports being contoured other than circular, said rotary valve member and casing forming a mixing chamber, closures for the ends of said casing, one of said closures being rotatable and connected to said valve member, an injection device disposed on the axis of said valve member and extending into the mixing chamber, said injec tion device comprising an outer injection member fixed to said rotatable closure and having its axis disposed on the axis of said valve member, the nozzle end of said injection member being disposed in said mixing chamber, a second injection member mounted in said outer injection member and having a nozzle end extending into the nozzle end of said outer injection member, said inner injection member having a closed end, and closing the end of said outer injection mem.- ber within said combustion chamber, said outer injection member being non-rotatable with respect to said cylindrical valve member, said nozzle ends having fuel ports for controlling the passage of fuel to said mixing chamber, said outer injection member having a plurality of similar contoured ports spaced apart equidistantly and of varying shape and disposed in a plane normal to the axis of said valve member, said outer injection member having a single port in a plane at an angle to the axis of said valve member, the entrance of the single port being disposed adjacent the end one of the contoured ports, said inner injection member having a single port of substantially circular section adapted to be controlled by the selected one of said contoured ports whereby a disproportionate opening of said last named single port is effected by a proportionate rotation of said cylindrical valve member and said outer injection member, said inner injection member having a plurality of equally spaced ports of substantially circular section in a plane normal to the axis of said circular valve member, the selected of said last named ports being controlled by said first named single port, rotation of the outer injection member rotating the valve member to vary the casing inlet and outlet and also rotate the ports of the outer injection member with respect to the ports of the inner injection member to vary the supply of fuel to said mixing chamber, and throttle means for simultaneously rotating the outer injection member and said valve member, rotation of the outer injection member and said valve member serving to regulate the fuel ports with respect to the casing inlet and outlet to maintain a selected air-fuel ratio during the entire operation of the throttle means.

3. In fuel metering mechanism for an internal combustion engine, the combination of a casing having an outlet adapted to be connected to the fuel mixture inlet of an internal combustion engine, said casing having an air inlet, said outlet and air inlet comprising coaxial passages of substantially circular section, the casing having a cylindrical bore the axis of which is substantially normal to the axis of said passages, a. cylindrical valve member rotatably mounted in said bore and provided with ports for controlling flow through said casing outlet and inlet, said rotary valve member and casing forming a mixing chamber, closures for the ends of said casing, one of said closures being rotatable and connected to said valve member, an injection device disposed on the axis of said valve member and extending into the mixing chamber, said injection device comprising an outer injection member fixed to said rotatable closure and having its axis disposed on the axis of said valve member, the nozzle end of said injection member being disposed in said mixing chamber, a second injection member mounted in said outer injection member and having a nozzle end extending into the nozzle end of said outer injection member, said outer injection member being non-rotatable with respect to said cylindrical valve member, said nozzle ends having fuel ports for controlling the passage of fuel to said mixing chamber, said outer injection member having a plurality of similar contoured ports spaced apart equidistantly and of varying shape and disposed in a plane normal to the axis of said valve member, said outer injection member having a single port in a plane at an angle to the axis of said valve member, the entrance of the single port being disposed adjacent the end one of the contoured ports, said inner injection member having a single port of substantially circular section adapted to be controlled by the selected one of said contoured ports whereby a disproportionate opening of said last named single port is effected by a proportionate rotation of said cylindrical valve member and said outer injection member, said inner injection member having a plurality of equally spaced ports of substantially circular section in a plane normal to the axis of said circular valve member, the selected of said last named ports being controlled by said first named single port, rotation of the outer injection member rotating the valve member to vary the casing inlet and outlet and also retate the ports of the outer injection member with respect to the ports of the inner injection member to vary the supply of fuel to said mixing chamber, and throttle means for simultaneously rotating the outer injection member and said valve member, rotation of the outer injection member and said valve member serving to regulate the fuel ports with respect to the casing inlet and outlet to maintain a selected air-fuel ratio during the entire operation of the throttle means.

4. In fuel metering mechanism for an internal combustion engine, the combination of a casing having an outlet adapted to be connected to the fuel mixture inlet of an internal combustion engine, said casing having an air inlet, the casinghaving a cylindrical bore, a cylindrical valve member rotatably mounted in said bore and provided with ports for controlling flow through said casing outlet and inlet, said rotary valve member and casing forming a mixing chamber, closures for the ends of said casing, one of said closures being rotatable and connected to said valve member, an injection device disposed on the axis of said valve member and extending into the mixing chamber, said injection device comprising an outer injection member fixed to said rotatable closure and having its axis disposed on the axis of said valve member, the nozzle end of said injection member being disposed in said mixing chamber, a second injection member mounted in said outer injection member and having a nozzle end extending into the nozzle end of said outer injection member, said outer injection member being non-rotatable with respect to said cylindrical valve member, said nozzle ends having fuel ports for controlling the passage of fuel to said mixing chamber, said outer injection member having a plurality of similar contoured ports spaced apart equidistantly and of varying shape and disposed in a plane normal to the axis of said valve member, said outer injection member having a single port in a plane at an angle to the axis of said valve member, the entrance of the single port being disposed adjacent the end one of the contoured ports, said inner injection member having a single port of substantially circular section adapted to be controlled by the selected one of said contoured ports whereby a disproportionate opening of said last named single port is effected by a proportionate rotation of said cylindrical valve member and said outerinjection member, said inner injection member having a plurality of equally spaced ports of substantially circular section in a plane normal to the axis of said circular valve member, the selected of said last named ports being controlled by said first named single port, rotation of the outer injection member rotating the valve member to vary the casing inlet and outlet and also rotate the ports of the outer injection member with respect to the ports of the inner injection member to vary the supply of fuel to said mixing chamber, an air supply line extending through said inner injection member and communicating with said mixing chamber, a baiile for directing the air from said last named supply line toward the operative of said first named contoured ports, a valve in said supply line operative when said cylindrical valve member is inoperative to admit air to the mixing chamber, and throttle means for simultaneously rotating the outer injection member and said valve member, rotation of the outer injection member and said valve member serving to regulate the fuel ports with respect to the casing inlet and outlet to maintain a selected air-fuel ratio during the entire operation of the throttle means and rendering the valve controlling the air supply line inoperative.

5. A fuel metering device in accordance with claim 1 wherein there is a control device comprising a casing having spaced chambers separated by spaced valve seats, a connection from one of said chambers to the outlet of said carburetor, a connection between said seats to said injection device, a connection from the other chamber to a source of fuel pressure supply, a collapsible bellows in said last named chamber having one 19 end connected to the carburetor outlet whereby suction tends to collapse said bellows, the other end of said bellows being connected to a valve having valve members adapted to close one of said seats, when the bellows is in collapsed condition the valve closing communication between the first named chamber and the fuel inlet, the bellows in fully extended position causing said valve to close communication between the fuel inlet and each of the other connections to the carburetor, the valve in intermediate position causing communication between each of said chambers.

EUGENE RIVOCHE.

RE ERENC S. CITED The following references are of record in the file of this. pat nt:

Number Number 20 UNITED STATES PATENTS Name Date Redman July 4, 1905 Best Feb. 1, 1910 Boyden Feb. 6, 1917 Yarnall Dec. 26, 1922 Leveque Nov. 13, 1928 Ferguson Aug. 26, 1941 Wirth Mar. 7, 1950 FOREIGN PATENTS Country Date Great Britain Publ. 1929, complete; not accepted Great Britain Feb. 7, 1939 

